JP2006152914A - Oil pump - Google Patents

Oil pump Download PDF

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Publication number
JP2006152914A
JP2006152914A JP2004344411A JP2004344411A JP2006152914A JP 2006152914 A JP2006152914 A JP 2006152914A JP 2004344411 A JP2004344411 A JP 2004344411A JP 2004344411 A JP2004344411 A JP 2004344411A JP 2006152914 A JP2006152914 A JP 2006152914A
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Japan
Prior art keywords
bearing
drive shaft
oil
groove
annular space
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JP2004344411A
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Japanese (ja)
Inventor
Shoji Morita
正二 盛田
Iwao Kondo
厳臣 近藤
Hideaki Onishi
秀明 大西
Yasushi Watanabe
靖 渡辺
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Hitachi Ltd
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Hitachi Ltd
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Priority to JP2004344411A priority Critical patent/JP2006152914A/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0088Lubrication
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16NLUBRICATING
    • F16N13/00Lubricating-pumps
    • F16N13/20Rotary pumps

Abstract

<P>PROBLEM TO BE SOLVED: To provide an oil pump improving lubrication performance of a bearing hole, especially a first bearing part, for bearing a drive shaft. <P>SOLUTION: The oil pump has the bearing hole 10 formed in a pump housing 1, and the drive shaft borne by the bearing hole. A cylindrical groove 11 constituting an annular space part 12 together with an outer circumferential face of the drive shaft is formed at an approximately middle position of an inner circumferential face of the bearing hole. The first bearing part 13 and a second bearing part 14 for rotatably supporting the drive shaft are formed at front and back end parts sandwiching the annular groove of the bearing hole therebetween, and an oil groove 15 making a discharge port 8 communicate with the annular space part 12 is formed in the inner circumferential face of the second bearing part. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、例えば、内燃機関のピストンや動弁装置などの各摺動部に潤滑油を供給するオイルポンプの改良に関する。   The present invention relates to an improvement in an oil pump that supplies lubricating oil to sliding parts such as a piston and a valve operating device of an internal combustion engine, for example.

例えば自動車用内燃機関の潤滑に用いられるオイルポンプとしては、一般にいわゆるトロコイドポンプが用いられており、その一例として以下の特許文献1に記載されているものが知られている。   For example, as an oil pump used for lubricating an internal combustion engine for automobiles, a so-called trochoid pump is generally used, and an example described in Patent Document 1 below is known.

概略を説明すれば、このオイルポンプは、ポンプハウジングの内部に形成された作動室に、内周側に複数の内歯が一体に形成されたアウターロータと、外周側に前記内歯に噛合する複数の外歯が一体に形成されたインナーロータと、前記インナーロータを回転駆動する駆動軸が回転自在に収容されている。   Briefly, this oil pump is meshed with an outer rotor in which a plurality of internal teeth are integrally formed on the inner peripheral side in an operation chamber formed inside the pump housing, and the inner teeth on the outer peripheral side. An inner rotor integrally formed with a plurality of external teeth and a drive shaft that rotationally drives the inner rotor are rotatably accommodated.

前記駆動軸を介してインナーロータが回転するに伴い前記内外歯間に形成されたポンプ室が容積を変化させて、吸入ポートからオイルを吸入すると共に吐出ポートから吐出してポンプ作用を行うようになっている。   As the inner rotor rotates via the drive shaft, the pump chamber formed between the inner and outer teeth changes its volume so that oil is sucked from the suction port and discharged from the discharge port to perform the pump action. It has become.

また、前記駆動軸は、前記ポンプハウジング内に形成された軸受孔の内周面で回転自在に支持されており、該駆動軸と軸受孔の間に、一端が前記吐出ポートに連通し、他端が軸受孔の途中で終わる第1の溝と、一端がポンプハウジングの外部側に連通し、他端が軸受孔の途中で終わる第2の溝が設けられている。   The drive shaft is rotatably supported by an inner peripheral surface of a bearing hole formed in the pump housing, and one end communicates with the discharge port between the drive shaft and the bearing hole. A first groove whose end ends in the middle of the bearing hole and a second groove whose one end communicates with the outside of the pump housing and whose other end ends in the middle of the bearing hole are provided.

この両溝は、相互に離間しかつ溝延出方向で、一部がオーバーラップするように配置されている。   The two grooves are arranged so as to be spaced apart from each other and partially overlap in the groove extending direction.

これによって、吐出ポートから流出したオイルは、前記第1の溝内に流入し、この第1の溝内から駆動軸の外周面と軸受孔の内周面との間を潤滑し、さらに前記オーバーラップ間の微小隙間を通って第2の溝内に流入して、ここで前記両内外周面間を潤滑するようになっている。
特開2003−239869号公報
As a result, the oil flowing out from the discharge port flows into the first groove, lubricates the space between the outer peripheral surface of the drive shaft and the inner peripheral surface of the bearing hole from within the first groove, and further It flows into the second groove through a minute gap between the wraps, and here, the space between the inner and outer peripheral surfaces is lubricated.
JP 2003-239869 A

しかしながら、前記従来のオイルポンプにあっては、前述のように、吐出ポートに連通する第1の溝には、オイルを速やかに供給することができるものの、この第1の溝は、軸方向へ細長く延出しているため、その断面積が小さい。したがって、該第1の溝内でのオイル貯留量を十分に確保することができず、この結果、駆動軸外周面と軸受孔内周面との間の潤滑性が不十分になるおそれがある。   However, in the conventional oil pump, as described above, although the oil can be quickly supplied to the first groove communicating with the discharge port, the first groove is formed in the axial direction. Because it is elongated, its cross-sectional area is small. Therefore, a sufficient amount of oil can not be secured in the first groove, and as a result, the lubricity between the outer peripheral surface of the drive shaft and the inner peripheral surface of the bearing hole may be insufficient. .

しかも、前記第2の溝には第1の溝から前記駆動軸外周面と軸受孔内周面との間の微小隙間からリークした僅かなオイルだけしか供給されない。したがって、軸受孔の外端側と駆動軸との間の潤滑性もさらに不十分になる。   In addition, only a small amount of oil leaking from the first groove through a minute gap between the outer peripheral surface of the drive shaft and the inner peripheral surface of the bearing hole is supplied to the second groove. Therefore, the lubricity between the outer end side of the bearing hole and the drive shaft is further insufficient.

このように軸受孔と駆動軸との間の潤滑性能の低下は、特にポンプ吐出流量の少ない機関始動時などに起こりやすい。   Thus, a decrease in the lubrication performance between the bearing hole and the drive shaft is likely to occur particularly when the engine is started with a small pump discharge flow rate.

本発明は、前記従来のオイルポンプの技術的課題に鑑みて案出されたもので、請求項1に記載の発明は、ポンプハウジング内の軸受孔と駆動軸との間に、前記ポンプハウジングの外端側に設けられて、前記駆動軸の軸方向の一部を回転自在に支持する第1軸受部と、前記ポンプ室側に設けられて、前記駆動軸の軸方向の一部を回転自在に支持する第2軸受部と、前記第1軸受部と第2軸受部との間に形成された環状空間部とをそれぞれ配置形成し、前記環状空間部を前記第2軸受部側から前記吐出ポートに連通させる連通部を形成したことを特徴としている。   The present invention has been devised in view of the technical problem of the conventional oil pump, and the invention according to claim 1 is characterized in that the pump housing is provided between the bearing hole in the pump housing and the drive shaft. A first bearing portion provided on the outer end side and rotatably supporting a part of the drive shaft in the axial direction, and provided on the pump chamber side and rotatable in a part of the drive shaft in the axial direction. A second bearing portion supported by the first bearing portion and an annular space portion formed between the first bearing portion and the second bearing portion, respectively, and discharging the annular space portion from the second bearing portion side. It is characterized in that a communication portion that communicates with a port is formed.

この発明によれば、オイルポンプの駆動に伴って吐出ポート内のオイルが連通部を介して第2軸受部と環状空間部内に供給されて、該環状空間部の円周方向の全体の部位から各軸受部にオイルが供給されるため、この部位のオイル供給不足が解消されて、各軸受部と駆動軸との間の潤滑性能が向上する。   According to the present invention, the oil in the discharge port is supplied to the second bearing portion and the annular space portion through the communicating portion as the oil pump is driven, and from the entire circumferential portion of the annular space portion. Since oil is supplied to each bearing portion, the shortage of oil supply at this portion is eliminated, and the lubrication performance between each bearing portion and the drive shaft is improved.

特に、前記環状空間部の容積が大きく、オイル貯留量も多くなることから、前記各軸受部への供給量も多くなるので、潤滑性能がさらに向上する。   In particular, since the volume of the annular space is large and the amount of oil stored is large, the amount of supply to the bearings is also large, so that the lubricating performance is further improved.

しかも、前記環状空間部の存在によって、前記駆動軸と軸受孔との間の摩擦抵抗が低減するため、駆動軸の回転性が良好になる。   Moreover, due to the presence of the annular space portion, the frictional resistance between the drive shaft and the bearing hole is reduced, so that the rotational performance of the drive shaft is improved.

請求項2に記載の発明は、前記第1軸受部と第2軸受部及び環状空間部を、前記軸受孔の内周面に形成したことを特徴としている。   The invention according to claim 2 is characterized in that the first bearing portion, the second bearing portion, and the annular space portion are formed on an inner peripheral surface of the bearing hole.

この発明によれば、前記環状空間部などを前記駆動軸の外周面に形成する必要がないので、該駆動軸の剛性、強度を高く維持することが可能になる。   According to the present invention, since it is not necessary to form the annular space portion or the like on the outer peripheral surface of the drive shaft, it is possible to maintain high rigidity and strength of the drive shaft.

請求項3に記載の発明は、前記第1軸受部と第2軸受部及び環状空間部を、前記駆動軸の外周面に形成したことを特徴としている。   The invention according to claim 3 is characterized in that the first bearing portion, the second bearing portion, and the annular space portion are formed on an outer peripheral surface of the drive shaft.

この発明によれば、駆動軸の外周面を加工することにより、環状空間部などを形成できるので、前記ハウジングの軸受孔の内周面を加工して形成する場合に比較して、その加工作業が容易になる。   According to the present invention, since the annular space portion or the like can be formed by processing the outer peripheral surface of the drive shaft, the processing work is compared with the case where the inner peripheral surface of the bearing hole of the housing is formed by processing. Becomes easier.

以下、本発明に係るオイルポンプの実施形態を図面に基づいて詳述する。本実施形態に供されるオイルポンプは、内燃機関のオイルパン内に配置されて、該内燃機関の各摺動部に潤滑油を供給するトロコイドポンプに適用したものである。 Hereinafter, an embodiment of an oil pump according to the present invention will be described in detail with reference to the drawings. The oil pump provided in this embodiment is applied to a trochoid pump that is disposed in an oil pan of an internal combustion engine and supplies lubricating oil to each sliding portion of the internal combustion engine.

すなわち、図1〜図4はオイルポンプの第1の実施形態を示し、一端開口がカバー部材2によって閉塞されたアルミ合金材からなるポンプハウジング1と、該ポンプハウジング1の内部に形成された環状の作動室1c内に回転自在に収容され、内周側に複数の内歯3aが周方向へ連続して形成されたアウターロータ3と、該アウターロータ3の内周側に回転自在に設けられ、外周側に前記内歯3aに噛合する外歯4aが周方向へ連続して形成されたインナーロータ4と、前記ポンプハウジング1内に回転自在に支持されて、前記インナーロータ4を一方向へ回転駆動させる駆動軸5と、前記内歯3aと外歯4aとの間に形成される複数のポンプ室6のうち、最大容積を有する閉じ込み部と最小容積を有する噛み合い部とを結ぶ軸線を中心にほぼ対称位置に設けられた吸入ポート7及び吐出ポート8とを備えている。   1 to 4 show a first embodiment of an oil pump, and a pump housing 1 made of an aluminum alloy material whose one end opening is closed by a cover member 2 and an annular formed inside the pump housing 1. The outer rotor 3 is rotatably accommodated in the working chamber 1c and has a plurality of inner teeth 3a formed continuously in the circumferential direction on the inner peripheral side, and is provided rotatably on the inner peripheral side of the outer rotor 3. The outer teeth 4a meshing with the inner teeth 3a on the outer peripheral side are continuously formed in the circumferential direction, and the inner rotor 4 is supported in one direction by being rotatably supported in the pump housing 1. Of the plurality of pump chambers 6 formed between the drive shaft 5 to be rotated and the inner teeth 3a and the outer teeth 4a, an axis line connecting the confined portion having the maximum volume and the meshing portion having the minimum volume is provided. In the center And a suction port 7 and discharge port 8 arranged at symmetrical positions.

前記ポンプハウジング1は、全体がほぼ段差円筒状に形成され、前記カバー部材2側の大径円環状のポンプ本体1aと、該ポンプ本体1aの端縁に一体に結合された小径な円筒部1bとから構成されており、前記ポンプ本体1aの内部に前記作動室1cが形成されていると共に、該作動室1c内の前記アウターロータ3とインナーロータ4を挟んだ前記ポンプ本体1aとカバー部材2の各内部に前記吸入ポート7と吐出ポート8が形成されている。   The pump housing 1 is formed in a substantially stepped cylindrical shape as a whole, and has a large-diameter annular pump body 1a on the cover member 2 side, and a small-diameter cylindrical portion 1b integrally coupled to an end edge of the pump body 1a. The working chamber 1c is formed inside the pump body 1a, and the pump body 1a and the cover member 2 sandwiching the outer rotor 3 and the inner rotor 4 in the working chamber 1c. The suction port 7 and the discharge port 8 are formed in the interior of each.

前記円筒部1bの外周面には、一端がポンプ本体1aの外端縁に結合され、他端が円筒部1bの先端まで延びた複数の補強リブ9が一体に設けられている。   A plurality of reinforcing ribs 9 having one end coupled to the outer end edge of the pump body 1a and the other end extending to the tip of the cylindrical portion 1b are integrally provided on the outer peripheral surface of the cylindrical portion 1b.

また、前記ポンプハウジング1の内部軸方向には、前記駆動軸5を回転自在に軸受する軸受孔10が貫通形成されている。   Further, a bearing hole 10 for rotatably bearing the drive shaft 5 is formed in the inner axial direction of the pump housing 1.

すなわち、この軸受孔10は、前記ポンプ本体1aの内部中央から円筒部1bの内部先端縁まで貫通形成され、内径が前記駆動軸5の外径よりも僅かに大きく設定されていると共に、内周面に筒状溝11が切欠形成され、この筒状溝11の底面と前記駆動軸5の外周面との間に円筒状の環状空間部12が構成されている。また、前記軸受孔10の前記環状空間部12の円筒部1bの先端側に、第1軸受部13が形成されていると共に、ポンプ本体1a側に、第2軸受部14がそれぞれ形成されている。   That is, the bearing hole 10 is formed so as to penetrate from the inner center of the pump main body 1a to the inner front end edge of the cylindrical portion 1b. The inner diameter is set slightly larger than the outer diameter of the drive shaft 5, and the inner circumference A cylindrical groove 11 is cut out on the surface, and a cylindrical annular space 12 is formed between the bottom surface of the cylindrical groove 11 and the outer peripheral surface of the drive shaft 5. Further, a first bearing portion 13 is formed on the distal end side of the cylindrical portion 1b of the annular space portion 12 of the bearing hole 10, and a second bearing portion 14 is formed on the pump body 1a side. .

前記筒状溝11、つまり環状空間部12は、軸受孔10の軸方向のほぼ中央位置に所定の軸方向の長さに形成され、したがって、その全体の容積が比較的大きく設定されていると共に、前記各軸受部13,14はその軸方向の長さがほぼ同一に設定されている。また、筒状溝11の溝深さは、円筒部1bの剛性を大きく低下させない程度の比較的浅く形成されている。   The cylindrical groove 11, that is, the annular space portion 12 is formed at a substantially axial position in the axial direction of the bearing hole 10 and has a predetermined axial length. Therefore, the overall volume is set to be relatively large. The bearing portions 13 and 14 are set to have substantially the same axial length. Moreover, the groove depth of the cylindrical groove | channel 11 is formed comparatively shallow so that the rigidity of the cylindrical part 1b may not be reduced significantly.

また、前記環状空間部12は、図2にも示すように、第2軸受部14の内周面及び該第2軸受部14の作動室1c側の端縁に連続して切欠形成されたほぼL字形状の連通部である油溝15によって前記吐出ポート8と連通している。   Further, as shown in FIG. 2, the annular space portion 12 is substantially formed by notching the inner peripheral surface of the second bearing portion 14 and the end edge on the working chamber 1 c side of the second bearing portion 14. The discharge port 8 communicates with an oil groove 15 which is an L-shaped communicating portion.

この油溝15は、ポンプハウジング1の鋳造後において鋳型から抜き出し易くするために、第2軸受部14の内周面に形成された部位15aが筒状溝11側から作動室1c側に掛けて拡径テーパー状に形成されている。   The oil groove 15 is formed so that a portion 15a formed on the inner peripheral surface of the second bearing portion 14 is hung from the cylindrical groove 11 side to the working chamber 1c side so that it can be easily extracted from the mold after the pump housing 1 is cast. It is formed in an enlarged taper shape.

なお、前記カバー部材2は、ポンプ本体1aの前端面に、図外のボルトによって固定されている。   The cover member 2 is fixed to the front end surface of the pump main body 1a with a bolt (not shown).

前記駆動軸5は、前記作動室1cに臨む一端部5aに前記インナーロータ4が中央の固定用孔4bを介してスプライン結合されていると共に、該一端部5a側が前記第2軸受部14に軸受されている一方、他端部5b側が前記第1軸受部13によって軸受されている。また、他端部5bの先端側には、外周に無端状のチェーンが巻回される従動スプロケット16がボルト17によって固定されている。前記従動スプロケット16は、前記無端状のチェーンを介して、図外の機関のクランク軸から回転力が伝達されるようになっている。   In the drive shaft 5, the inner rotor 4 is splined to one end portion 5a facing the working chamber 1c via a central fixing hole 4b, and the one end portion 5a side is supported by the second bearing portion 14. On the other hand, the other end portion 5 b side is supported by the first bearing portion 13. Further, a driven sprocket 16 around which an endless chain is wound around the outer periphery is fixed by a bolt 17 at the tip end side of the other end 5b. The driven sprocket 16 is adapted to transmit a rotational force from a crankshaft of an engine (not shown) through the endless chain.

したがって、このオイルポンプにあっては、機関の始動後に駆動軸5の回転駆動に伴いインナーロータ4とアウターロータ3が回転してポンプ作用が行われ、吐出ポート8内のオイルが油溝15を介して第2軸受部14と環状空間部12内に供給される。このため、油溝15が形成された第2軸受部14は勿論のこと、油溝のない第1軸受部13の潤滑性能が大幅に向上する。   Therefore, in this oil pump, the inner rotor 4 and the outer rotor 3 are rotated by the rotational drive of the drive shaft 5 after the engine is started to perform the pump action, and the oil in the discharge port 8 flows through the oil groove 15. Via the second bearing portion 14 and the annular space portion 12. For this reason, the lubricating performance of the 1st bearing part 13 without an oil groove not to mention the 2nd bearing part 14 in which the oil groove 15 was formed improves significantly.

すなわち、前記環状空間部12は、円環状であり、その容積が大きく形成されてオイル貯留量も多くなることから、該各環状空間部12の両端側の環状部12a、12bから第1、第2軸受部13,14の各内周面と駆動軸5の外周面との間の環状な微小クリアランスの全体に軸方向からオイルを供給することができる。このため、駆動軸5の一端部5a及び他端部5bと各第1,2軸受部13,14との間の潤滑性能が向上する。   That is, the annular space portion 12 is annular and has a large volume and a large oil storage amount. Therefore, the annular portions 12a and 12b on both ends of each annular space portion 12 are first to first, The oil can be supplied from the axial direction to the entire annular minute clearance between the inner peripheral surfaces of the two bearing portions 13 and 14 and the outer peripheral surface of the drive shaft 5. For this reason, the lubrication performance between the one end part 5a and the other end part 5b of the drive shaft 5 and the first and second bearing parts 13 and 14 is improved.

しかも、前記環状空間部12の存在によって、前記駆動軸5と軸受孔10とのかかる部位の接触が回避されることから、摩擦抵抗が低減する。したがって、駆動軸5の回転性が良好になる。   In addition, the presence of the annular space portion 12 avoids contact between the drive shaft 5 and the bearing hole 10, thereby reducing frictional resistance. Therefore, the rotational property of the drive shaft 5 is improved.

また、この実施形態では、前記筒状溝11などを前記駆動軸5の外周面に形成するのではなく、ポンプハウジング1の軸受孔10の内周面に形成したため、前記駆動軸5の剛性強度を高く維持することが可能になる。   In this embodiment, the cylindrical groove 11 and the like are not formed on the outer peripheral surface of the drive shaft 5 but are formed on the inner peripheral surface of the bearing hole 10 of the pump housing 1. Can be kept high.

図5は本発明の第2の実施形態を示し、この実施形態も基本構造は前記第1の実施形態と同様であるが、異なるところは、前記第1軸受部13の内周面に前記環状空間部12と連通する連通溝18を形成したものである。   FIG. 5 shows a second embodiment of the present invention. The basic structure of this embodiment is the same as that of the first embodiment, except that the annular shape is formed on the inner peripheral surface of the first bearing portion 13. A communication groove 18 communicating with the space portion 12 is formed.

すなわち、前記連通溝18は、前記油溝15とほぼ直列状態で同方向に細長く形成され、一端側18aが前記筒状溝11の一端縁に開口形成され、他端側18bが第1軸受部13の軸方向のほぼ3分の2まで延長されて軸方向の途中で閉止されている。   That is, the communication groove 18 is formed to be elongated in the same direction in a substantially series state with the oil groove 15, one end side 18 a is formed to open at one end edge of the cylindrical groove 11, and the other end side 18 b is the first bearing portion. 13 is extended to approximately two thirds of the axial direction and closed in the middle of the axial direction.

したがって、この実施形態によれば、前記環状空間部12内に供給されたオイルは、連通溝18内にそのまま供給され、該連通溝18から第1軸受部13の全体に前記環状空間部12内のオイルと共に速やかに行き渡らせることが可能になる。この結果、該第1軸受部13の潤滑性能をさらに向上させることができる。   Therefore, according to this embodiment, the oil supplied into the annular space portion 12 is supplied as it is into the communication groove 18, and the entire first bearing portion 13 extends from the communication groove 18 to the inside of the annular space portion 12. It becomes possible to spread quickly with the oil. As a result, the lubricating performance of the first bearing portion 13 can be further improved.

また、前記他端側18bが第1軸受部13の内周面の途中で止められていることから、環状空間部12から連通溝18内に流入したオイルの流動がここで遮断されるので、オイルポンプの吐出効率に影響を与えることがない。   Further, since the other end side 18b is stopped in the middle of the inner peripheral surface of the first bearing portion 13, the flow of oil flowing into the communication groove 18 from the annular space portion 12 is blocked here. Does not affect the discharge efficiency of the oil pump.

なお、前記連通溝18は、必ずしも軸方向に沿って形成する必要はなく、例えば螺旋状あるいは傾斜状に形成することも可能であり、このように形成すれば、駆動軸5の回りをさらに効果的に潤滑することが可能になる。但し、他端側は、前述のように必ず第1軸受部13の途中で止められていなければならない。   The communication groove 18 is not necessarily formed along the axial direction, and can be formed, for example, in a spiral shape or an inclined shape. Lubrication. However, the other end side must be stopped in the middle of the first bearing portion 13 as described above.

図6は第3の実施形態を示し、第1の実施形態と異なるところは、前記筒状溝11の形成位置を第2軸受部14側に移動して、第1軸受部13の軸方向の長さLを第2軸受部14の軸方向の長さL1よりも大きく設定したものである。   FIG. 6 shows the third embodiment. The difference from the first embodiment is that the formation position of the cylindrical groove 11 is moved to the second bearing portion 14 side, and the axial direction of the first bearing portion 13 is changed. The length L is set larger than the length L1 of the second bearing portion 14 in the axial direction.

前記駆動軸5には、前記クランク軸から前記チェーンや従動スプロケット16などを介して回転駆動力が伝達されるが、この回転駆動力の伝達に伴って先端側、つまり第1軸受部13側の外端部側に径方向(矢印方向)のテンションが作用して大きな回転モーメントが作用する場合がある。このため、前記第1軸受部13は、駆動軸5の前記大きな回転モーメントを受けなければならない。   A rotational driving force is transmitted from the crankshaft to the drive shaft 5 through the chain, the driven sprocket 16 and the like. The transmission of the rotational driving force causes the distal end side, that is, the first bearing portion 13 side. There is a case where a large rotational moment acts due to a radial (arrow direction) tension acting on the outer end side. For this reason, the first bearing portion 13 must receive the large rotational moment of the drive shaft 5.

したがって、この実施形態のように、第1軸受部13の軸方向の長さLを大きくすることによって、該第1軸受部13の剛性が高くなるので、駆動軸5を安定に支持することが可能になる。   Therefore, since the rigidity of the first bearing portion 13 is increased by increasing the axial length L of the first bearing portion 13 as in this embodiment, the drive shaft 5 can be stably supported. It becomes possible.

図7は第4の実施形態を示し、この実施形態では、前記筒状溝11を、軸受孔10の内周面ではなく、駆動軸5の外周面に形成したものである。   FIG. 7 shows a fourth embodiment. In this embodiment, the cylindrical groove 11 is formed not on the inner peripheral surface of the bearing hole 10 but on the outer peripheral surface of the drive shaft 5.

すなわち、前記駆動軸5のポンプハウジング1の円筒部1b内に位置する外周面に、円筒状の筒状溝11が形成され、該筒状溝11の底面と前記軸受孔10の内周面との間に環状空間部12が形成されている。そして、前記環状空間部12の前後位置の軸受孔10に第1軸受部13と第2軸受部14が形成されている。   That is, a cylindrical cylindrical groove 11 is formed on the outer peripheral surface of the drive shaft 5 located in the cylindrical portion 1b of the pump housing 1, and the bottom surface of the cylindrical groove 11 and the inner peripheral surface of the bearing hole 10 are formed. An annular space 12 is formed between the two. And the 1st bearing part 13 and the 2nd bearing part 14 are formed in the bearing hole 10 of the front-back position of the said annular space part 12. As shown in FIG.

このように、駆動軸5の外周面に筒状溝11を形成することによって、環状空間部12や第1、第2軸受部13,14を形成できるので、前記軸受孔10の内周面を加工して形成する場合に比較して、その加工作業が容易になる。   Thus, by forming the cylindrical groove 11 on the outer peripheral surface of the drive shaft 5, the annular space portion 12 and the first and second bearing portions 13 and 14 can be formed, so that the inner peripheral surface of the bearing hole 10 is formed. Compared with the case of forming by processing, the processing work becomes easier.

図8は第5の実施形態を示し、第1軸受部と第2軸受部を軸受ブッシュ19,20によって構成したものである。   FIG. 8 shows a fifth embodiment in which the first bearing portion and the second bearing portion are constituted by bearing bushes 19 and 20.

具体的に説明すれば、前記軸受孔10の内径が前記各実施形態のものよりも僅かに大きく設定され、該軸受孔10の前後端部に前記第1、第2軸受ブッシュ19,20が圧入固定され、この両軸受ブッシュ19,10の内周面で前記駆動軸5を軸受するように構成されている。   More specifically, the inner diameter of the bearing hole 10 is set to be slightly larger than those of the respective embodiments, and the first and second bearing bushes 19 and 20 are press-fitted into the front and rear end portions of the bearing hole 10. The drive shaft 5 is supported by the inner peripheral surfaces of the two bearing bushes 19 and 10.

前記各軸受ブッシュ19,10は、硬質な合成樹脂材などによってほぼ円筒状に形成され、両者の軸方向の長さがほぼ同一に設定され、外周部が前記軸受孔10の内周面の軸方向の前後端部に一定の間隔を置いて圧入固定されている。したがって、該両軸受ブッシュ19,20の対向する端縁の間に円筒状の環状空間部12が形成されることになる。   Each of the bearing bushes 19 and 10 is formed in a substantially cylindrical shape by a hard synthetic resin material or the like, both axial lengths thereof are set to be substantially the same, and the outer peripheral portion is an axis of the inner peripheral surface of the bearing hole 10. It is press-fitted and fixed at a certain interval at the front and rear ends of the direction. Therefore, the cylindrical annular space 12 is formed between the opposing edges of the bearing bushes 19 and 20.

また、前記環状空間部12と連通する油溝15は、作動室1c側に臨む径方向の一端部15aが前記吐出ポート8に開口していることは前記各実施形態と同様であるが、軸方向の他端部15bが前記第2軸受ブッシュ20の外面側の前記軸受孔10の内周面に形成されている。   In addition, the oil groove 15 communicating with the annular space portion 12 is the same as in each of the above embodiments in that the radial end portion 15a facing the working chamber 1c is open to the discharge port 8. The other end 15 b in the direction is formed on the inner peripheral surface of the bearing hole 10 on the outer surface side of the second bearing bush 20.

したがって、この実施形態によれば、各構成部品の組付時に各軸受ブッシュ19,20を軸受孔10の内周面と駆動軸5の外周面との間に挿着させれば良いので、前記軸受孔10や駆動軸5に特別な加工作業が不要になることから、製造作業が容易になる。   Therefore, according to this embodiment, the bearing bushes 19 and 20 may be inserted between the inner peripheral surface of the bearing hole 10 and the outer peripheral surface of the drive shaft 5 when assembling each component. Since no special processing work is required for the bearing hole 10 or the drive shaft 5, the manufacturing work is facilitated.

また、前記油溝15の他端部15bを、軸受孔10に形成して第2軸受ブッシュ20には形成しないことから、各軸受ブッシュ19,20の共用化が図れる。   Further, since the other end 15b of the oil groove 15 is formed in the bearing hole 10 but not in the second bearing bush 20, the bearing bushes 19 and 20 can be shared.

図9は第6の実施形態を示し、前記軸受孔10の内周面の外端側及び前記作動室1c側に円筒状の保持溝21,22がそれぞれ形成されていると共に、該各保持溝21,22に前記各軸受ブッシュ19,20が嵌合保持されている。   FIG. 9 shows a sixth embodiment, in which cylindrical holding grooves 21 and 22 are respectively formed on the outer end side of the inner peripheral surface of the bearing hole 10 and the working chamber 1c side. The bearing bushes 19 and 20 are fitted and held on 21 and 22, respectively.

また、第2軸受ブッシュ20の内周面に軸方向に沿った切欠溝を形成し、この切欠溝によって前記油溝15の他端部15bを構成したものである。   Further, a notch groove along the axial direction is formed on the inner peripheral surface of the second bearing bush 20, and the other end portion 15 b of the oil groove 15 is configured by this notch groove.

したがって、各軸受ブッシュ19,20を各保持溝21,22内に嵌合保持したことによって、該各軸受ブッシュ21,22を安定かつ確実に位置決め保持することが可能になる。   Accordingly, the bearing bushes 19 and 20 are fitted and held in the holding grooves 21 and 22, respectively, so that the bearing bushes 21 and 22 can be positioned and held stably.

また、油溝15の他端部15bを第2軸受ブッシュ20の内周面に形成したことから、前記軸受孔10の内周面などに形成する必要がなくなるので、この点で加工作業が容易になる。   Further, since the other end portion 15b of the oil groove 15 is formed on the inner peripheral surface of the second bearing bush 20, it is not necessary to form the other end portion 15b on the inner peripheral surface of the bearing hole 10 or the like. become.

前記実施形態から把握される前記請求項に記載した発明以外の技術的思想について以下に説明する。   The technical ideas other than the invention described in the claims, as grasped from the embodiment, will be described below.

請求項(1) 前記第1軸受部に前記環状空間部と連通させる連通溝を軸方向の途中位置まで形成したことを特徴とする請求項1〜3のいずれかに記載のオイルポンプ。   (1) The oil pump according to any one of claims 1 to 3, wherein a communication groove that communicates with the annular space portion is formed in the first bearing portion up to an intermediate position in the axial direction.

前記環状空間部に供給されたオイルは、連通溝内にそのまま供給され、該連通溝から第1軸受部全体に速やかに行き渡らせることが可能になる。この結果、該第1軸受部の潤滑性能をさらに向上させることができる。   The oil supplied to the annular space portion is supplied as it is into the communication groove, and can be quickly distributed from the communication groove to the entire first bearing portion. As a result, the lubricating performance of the first bearing portion can be further improved.

請求項(2) 前記第1軸受部と第2軸受部を、軸受ブッシュによってそれぞれ形成したことを特徴とする請求項1〜(1)のいずれかに記載のオイルポンプ。   (2) The oil pump according to any one of (1) to (1), wherein each of the first bearing portion and the second bearing portion is formed by a bearing bush.

この発明では、各構成部品の組付時に軸受ブッシュを軸受孔と駆動軸との間に挿着させれば良いので、前記軸受孔や駆動軸の加工作業が容易になる。   According to the present invention, since the bearing bush may be inserted between the bearing hole and the drive shaft at the time of assembling each component, the machining operation of the bearing hole and the drive shaft is facilitated.

請求項(3) 前記各軸受ブッシュを、前記軸受孔の内周面と駆動軸の外周面との間に軸方向へ所定間隔をおいて配置すると共に、該両軸受ブッシュの間に、前記環状空間部を形成したことを特徴とする請求項(2)に記載のオイルポンプ。   (3) The bearing bushes are arranged at a predetermined interval in the axial direction between the inner peripheral surface of the bearing hole and the outer peripheral surface of the drive shaft, and the annular ring is formed between the bearing bushes. The oil pump according to claim 2, wherein a space is formed.

この発明によれば、ハウジングの軸受孔の内周面や駆動軸の外周面を何ら加工することなく、各軸受部や環状空間部を形成することができるので、製造作業が容易になる。   According to the present invention, since each bearing portion and the annular space portion can be formed without processing the inner peripheral surface of the bearing hole of the housing and the outer peripheral surface of the drive shaft, the manufacturing operation is facilitated.

請求項(4) 前記軸受孔の内周面の外端側及び前記ポンプ室側に円環状の保持溝をそれぞれ形成すると共に、該各保持溝に前記各軸受ブッシュを嵌合保持したことを特徴とする請求項(2)に記載のオイルポンプ。   (4) An annular holding groove is formed on the outer end side of the inner peripheral surface of the bearing hole and the pump chamber side, and the bearing bushes are fitted and held in the holding grooves. The oil pump according to claim (2).

この発明によれば、各軸受ブッシュを各保持溝内に嵌合保持したことによって、該各軸受ブッシュを安定かつ確実に位置決め保持することが可能になる。   According to the present invention, since each bearing bush is fitted and held in each holding groove, each bearing bush can be positioned and held stably and reliably.

請求項(5) 第2軸受ブッシュの内周面に、前記吐出ポートと環状空間部を連通する連通部を形成したことを特徴とする請求項(2)〜(4)のいずれかに記載のオイルポンプ。   (5) The communication portion according to any one of (2) to (4), wherein a communication portion that communicates the discharge port and the annular space portion is formed on an inner peripheral surface of the second bearing bush. Oil pump.

連通部を第2軸受ブッシュに形成したことから、前記軸受孔の内周面などに形成する必要がなくなるので、加工作業が容易になる。   Since the communication portion is formed on the second bearing bush, it is not necessary to form the communication portion on the inner peripheral surface of the bearing hole, and the machining operation is facilitated.

請求項(6) 前記連通部を前記軸受孔に形成したことを特徴とする請求項(2)〜(4)のいずれかに記載のオイルポンプ。   (6) The oil pump according to any one of (2) to (4), wherein the communication portion is formed in the bearing hole.

この発明によれば、各軸受ブッシュ側には連通部を形成しないことから、各軸受ブッシュの共用化が図れる。   According to the present invention, since the communication portion is not formed on each bearing bush side, each bearing bush can be shared.

請求項(7) 前記第1軸受部の軸方向の長さを前記第2軸受部の軸方向の長さよりも大きく形成したことを特徴とする請求項1〜(6)のいずれかに記載のオイルポンプ。   (7) The axial length of the first bearing portion is formed larger than the axial length of the second bearing portion, according to any one of claims 1 to (6). Oil pump.

前記駆動軸には、例えば内燃機関のクランク軸からスプロケットやチェーンなどを介して回転駆動力が伝達されるが、この回転駆動力の伝達に伴って先端側、つまり第1軸受部側の端部に径方向のテンションが作用して大きな回転モーメントが作用する場合がある。このため、前記第1軸受部は、駆動軸の前記大きな回転モーメントを受けなければならないことから、この軸方向の長さを大きくすることによって、駆動軸を安定に支持することが可能になる。   A rotational driving force is transmitted to the driving shaft from, for example, a crankshaft of an internal combustion engine via a sprocket, a chain, or the like. In some cases, a large rotational moment may be applied due to the radial tension. For this reason, since the first bearing portion must receive the large rotational moment of the drive shaft, the drive shaft can be stably supported by increasing the length in the axial direction.

請求項(8) 内部に円環状の作動室が形成されたハウジングと、
前記作動室の内部に回転自在に収容され、内周側に複数の内歯が形成されたアウターロータと、
該アウターロータの内周側に回転自在に設けられ、外周側に前記内歯に噛合する外歯が形成されたインナーロータと、
該インナーロータを回転駆動する前記駆動軸と、
前記内歯と外歯との間に形成される複数の前記ポンプ室と、
前記複数のポンプ室に開口する吸入ポート及び前記吐出ポートと、
を備えたことを特徴とする請求項1〜(7)のいずれかに記載のオイルポンプ。
(8) A housing having an annular working chamber formed therein;
An outer rotor that is rotatably accommodated in the working chamber and has a plurality of inner teeth formed on the inner peripheral side;
An inner rotor that is rotatably provided on the inner peripheral side of the outer rotor, and has outer teeth that are engaged with the inner teeth on the outer peripheral side;
The drive shaft for rotationally driving the inner rotor;
A plurality of the pump chambers formed between the inner teeth and the outer teeth;
A suction port opening to the plurality of pump chambers and the discharge port;
The oil pump according to any one of claims 1 to 7, wherein the oil pump is provided.

本発明は前記実施形態の構成に限定されるものではなく、オイルポンプの適用対象として、例えば、車両のパワーステアリング装置やブレーキ装置の油圧源として用いることも可能である。   The present invention is not limited to the configuration of the above-described embodiment, and can be used as an oil pump application target, for example, as a hydraulic power source of a vehicle power steering device or a brake device.

また、前記各実施形態では駆動軸の一端部側の軸受構造について説明したが、駆動軸の両端部側を軸受するものに適用することも可能である。   In each of the above embodiments, the bearing structure on the one end portion side of the drive shaft has been described. However, the present invention can also be applied to a structure that supports both end portions of the drive shaft.

本発明に係るオイルポンプの第1の実施形態を示す図3のA−A線断面図である。It is the sectional view on the AA line of FIG. 3 which shows 1st Embodiment of the oil pump which concerns on this invention. 本実施形態に供されるポンプハウジングの要部縦断面図である。It is a principal part longitudinal cross-sectional view of the pump housing provided to this embodiment. 本実施形態にかかるオイルポンプのカバー部材を外して示す正面図である。It is a front view which removes and shows the cover member of the oil pump concerning this embodiment. 本実施形態にかかるポンプハウジングの正面図である。。It is a front view of the pump housing concerning this embodiment. . 第2の実施形態に供されるポンプハウジングの要部縦断面図である。It is a principal part longitudinal cross-sectional view of the pump housing provided to 2nd Embodiment. 第3の実施形態にかかるオイルポンプの縦断面図ある。It is a longitudinal cross-sectional view of the oil pump concerning 3rd Embodiment. 第4の実施形態にかかるオイルポンプの縦断面図である。It is a longitudinal cross-sectional view of the oil pump concerning 4th Embodiment. 第5の実施形態にかかるオイルポンプの縦断面図である。It is a longitudinal cross-sectional view of the oil pump concerning 5th Embodiment. 第6の実施形態にかかるオイルポンプの縦断面図である。It is a longitudinal cross-sectional view of the oil pump concerning 6th Embodiment.

符号の説明Explanation of symbols

1…ポンプハウジング
1c…作動室
3…アウターロータ
4…インナーロータ
5…駆動軸
7…吸入ポート
8…吐出ポート
10…軸受孔
11…筒状溝
12…環状空間部
13…第1軸受部
14…第2軸受部
15…油溝(連通部)
18…連通溝
19・20…軸受ブッシュ(第1,第2軸受部)
21・22…保持溝
DESCRIPTION OF SYMBOLS 1 ... Pump housing 1c ... Working chamber 3 ... Outer rotor 4 ... Inner rotor 5 ... Drive shaft 7 ... Intake port 8 ... Discharge port 10 ... Bearing hole 11 ... Cylindrical groove 12 ... Annular space part 13 ... 1st bearing part 14 ... Second bearing portion 15 ... oil groove (communication portion)
18 ... Communication groove 19/20 ... Bushing bush (first and second bearing parts)
21.22 ... Holding groove

Claims (3)

ポンプハウジングに設けられた軸受孔と、該軸受孔に軸受された駆動軸とを備え、該駆動軸が回転駆動することによってポンプ室内で加圧されたオイルを吐出ポートを介して吐出するオイルポンプにおいて、
前記軸受孔と駆動軸との間に、前記ポンプハウジングの外端側に設けられて、前記駆動軸の軸方向の一部を回転自在に支持する第1軸受部と、前記ポンプ室側に設けられて、前記駆動軸の軸方向の一部を回転自在に支持する第2軸受部と、前記第1軸受部と第2軸受部との間に形成された環状空間部とをそれぞれ配置形成し、
前記環状空間部を前記第2軸受部側から前記吐出ポートに連通させる連通部を形成したことを特徴とするオイルポンプ。
An oil pump having a bearing hole provided in a pump housing and a drive shaft that is supported by the bearing hole, and discharging oil pressurized in the pump chamber through a discharge port when the drive shaft is driven to rotate. In
A first bearing portion provided on the outer end side of the pump housing between the bearing hole and the drive shaft and rotatably supporting a part of the axial direction of the drive shaft, and provided on the pump chamber side A second bearing portion that rotatably supports a part of the drive shaft in the axial direction, and an annular space portion formed between the first bearing portion and the second bearing portion. ,
An oil pump characterized in that a communicating portion is formed for communicating the annular space portion with the discharge port from the second bearing portion side.
前記第1軸受部と第2軸受部及び環状空間部を、前記軸受孔の内周面に形成したことを特徴とする請求項1に記載のオイルポンプ。 The oil pump according to claim 1, wherein the first bearing portion, the second bearing portion, and the annular space portion are formed on an inner peripheral surface of the bearing hole. 前記第1軸受部と第2軸受部及び環状空間部を、前記駆動軸の外周面に形成したことを特徴とする請求項1に記載のオイルポンプ。
The oil pump according to claim 1, wherein the first bearing portion, the second bearing portion, and the annular space portion are formed on an outer peripheral surface of the drive shaft.
JP2004344411A 2004-11-29 2004-11-29 Oil pump Pending JP2006152914A (en)

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JP2004344411A JP2006152914A (en) 2004-11-29 2004-11-29 Oil pump
DE200510052346 DE102005052346A1 (en) 2004-11-29 2005-11-02 Oil pump for internal combustion engine, has pump housing and drive that are cooperated in such a manner that it forms circular cavity between bearing journal sections, and connecting duct section arranged in one of sections
US11/287,320 US8075284B2 (en) 2004-11-29 2005-11-28 Oil pump

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